CN107035586B - Micro-dynamic oil return resonant type electric control oil injector with hydraulic feedback - Google Patents
Micro-dynamic oil return resonant type electric control oil injector with hydraulic feedback Download PDFInfo
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- CN107035586B CN107035586B CN201710034958.6A CN201710034958A CN107035586B CN 107035586 B CN107035586 B CN 107035586B CN 201710034958 A CN201710034958 A CN 201710034958A CN 107035586 B CN107035586 B CN 107035586B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
- F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
- F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
- F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/1893—Details of valve member ends not covered by groups F02M61/1866 - F02M61/188
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0014—Valves characterised by the valve actuating means
- F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
- F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
- F02M63/0035—Poppet valves, i.e. having a mushroom-shaped valve member that moves perpendicularly to the plane of the valve seat
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
- F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
- F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations
Abstract
The invention aims to provide a fretting state oil return resonance type electric control oil injector with hydraulic feedback, which comprises an oil injector head, an oil injector body, a flow limiting valve component, an electromagnetic valve component and a needle valve body. The pressure storage cavity is arranged in the oil sprayer body and communicated with the main oil inlet hole and the flow limiting valve assembly, so that the stability of the oil spraying process of each cylinder is guaranteed under the condition of large oil spraying quantity. The flow-limiting valve assembly is placed below the pressure accumulation cavity, and abnormal oil injection is prevented from being continuously performed. The bottom of the flow limiting valve assembly is provided with a resonance through hole and a resonance throttling hole, and the fluctuation of fuel oil passing through the flow limiting valve assembly is reduced by utilizing the wave superposition principle. The bottom of the oil sprayer body is provided with an electromagnetic valve assembly, a balance valve rod is driven to move by electromagnetic force, an annular throttle belt and an oil inlet throttle hole at the conical surface of the balance valve rod are matched with a hydraulic feedback oil duct to realize the variable oil spraying rule from slow to fast at the beginning of oil spraying, and the seating response of a needle valve is accelerated. The static pressure difference does not exist in the oil sprayer, the oil sprayer does not have static leakage, and the hydraulic efficiency of the system is improved.
Description
Technical Field
The invention relates to an engine fuel injection device.
Background
At present, most of the adopted electric control oil injectors adopt two-position two-way high-speed electromagnetic valves to control the oil injection process. In order to ensure the normal injection of the fuel injector, the diameter of the oil outlet throttling hole of the fuel injector needs to be larger than that of the oil inlet throttling hole, and the diameter of the oil inlet throttling hole needs to be increased to further improve the seating response characteristic of the needle valve, so that the dynamic oil return amount is increased, and the energy loss is caused. Conversely, decreasing the outlet orifice diameter to reduce the dynamic return flow slows the control chamber pressure build-up, causing a delay in needle seating. Therefore, the dynamic oil return amount of the electric control oil injector in the form of the two-position two-way valve is large, the fuel oil utilization rate is influenced, and the improvement of the response characteristic of the needle valve is limited. Because the oil sprayer mostly adopts a form of combining a control plunger matching part and a needle valve matching part, a static leakage exists in an axial sealing surface between the control plunger matching part and the needle valve matching part, the hydraulic efficiency of a system is reduced, and the further lifting of the pressure of the oil sprayer is limited; in addition, the quick opening and closing of the oil injector can generate water hammer pressure fluctuation, the stability of the oil injection process is reduced, common rail pressure fluctuation is easily caused in the large-oil-quantity injection process, and the uniformity of the oil injection process of each cylinder is reduced.
Disclosure of Invention
The invention aims to provide a micro-dynamic oil return resonant type electric control oil injector with hydraulic feedback, which has small dynamic oil return amount, can realize variable oil injection rule and has no static leakage function.
The purpose of the invention is realized as follows:
the invention relates to a micro-dynamic oil return resonant type electric control oil injector with hydraulic feedback, which is characterized in that: the oil sprayer comprises an oil sprayer head, an oil sprayer body, a flow limiting valve assembly, a solenoid valve assembly, a needle valve assembly and a downlink high-pressure oil way, wherein the oil sprayer head is arranged above the oil sprayer body, a main oil inlet hole is formed in the oil sprayer head, a pressure storage cavity is formed in the oil sprayer body, the main oil inlet hole is communicated with the pressure storage cavity, the flow limiting valve assembly is arranged in the pressure storage cavity, the solenoid valve assembly and the needle valve assembly are sequentially arranged at the lower end of the oil sprayer body, a tightening cap is positioned outside the solenoid valve assembly and the needle valve assembly, and the upper end of the tightening cap is connected with the lower end of the oil sprayer body in a threaded connection mode;
the flow limiting valve assembly comprises a limiting spring seat, a flow limiting piston, a ball valve reset spring seat and a supporting slide block, wherein the limiting spring seat, the flow limiting piston and the ball valve reset spring seat are arranged from top to bottom;
the electromagnetic valve assembly comprises an electromagnet, a coil, an armature, a balance valve rod, a valve seat and an intermediate block, wherein the coil is wound on the electromagnet, an electromagnetic valve reset spring seat is arranged above the electromagnet, the armature is arranged below the electromagnet, an electromagnetic valve reset spring is arranged between the armature and the electromagnetic valve reset spring seat, the balance valve rod is positioned in the valve seat, the upper end part of the balance valve rod is fixedly connected with the armature, the intermediate block is arranged below the valve seat, a balance valve rod upper cavity is formed between the middle part of the balance valve rod and the valve seat, an oil cavity is formed between the lower end part of the balance valve rod, the valve seat and the intermediate block, an oil inlet orifice is arranged in the valve seat, an oil return hole, the intermediate oil channel and a hydraulic feedback oil channel are arranged in the intermediate block, the oil inlet orifice is communicated with the balance valve rod upper cavity, the intermediate oil channel and the hydraulic feedback oil channel are respectively communicated with or disconnected with the oil tank under the control of the balance valve rod;
the needle valve assembly comprises a needle valve limiting sleeve, a nozzle and a needle valve body, the needle valve limiting sleeve is positioned in the nozzle, the upper part of the needle valve body is positioned in the needle valve limiting sleeve, the lower part of the needle valve body is positioned in the nozzle, a control cavity is formed between the upper part of the needle valve body and the needle valve limiting sleeve, a bulge is arranged on the needle valve limiting sleeve and positioned at the control cavity, a needle valve reset spring is arranged between the needle valve body and the bulge, the control cavity is communicated with a middle oil duct, an oil containing groove is formed between the needle valve body and the nozzle, and the end part of the nozzle is provided with a spray hole;
the upper end of the descending high-pressure oil way is communicated with a transition oil cavity and is communicated with an oil containing groove through an oil injector body, a valve seat, a middle block and a nozzle, and an oil inlet throttling hole and a hydraulic feedback oil way are respectively communicated with the descending high-pressure oil way.
The present invention may further comprise:
1. when the spray hole sprays oil, the fuel pressure of the transition oil cavity is reduced, the flow-limiting piston, the ball valve and the supporting slide block integrally move downwards, the ball valve is not seated on the ball valve reset spring seat, and the flow-limiting hole is communicated with the axial central through hole; when the mass of the fuel flowing out of the spray hole exceeds a threshold value, the flow limiting piston compresses the ball valve and enables the ball valve to be seated on a ball valve reset spring seat, and the flow limiting hole is disconnected with the axial central through hole; when the spray hole stops spraying oil, the flow-limiting piston, the ball valve and the supporting slide block are integrally restored to the initial positions under the action of the ball valve return spring.
2. When the coil is electrified, the balance valve rod moves upwards, the upper cavity of the balance valve rod is in a disconnected state with the oil cavity, the oil return hole is in a communicated state with the oil tank, fuel oil in the control cavity returns to the oil tank through the middle oil duct and the oil return hole, the needle valve body is lifted upwards, and the spray hole is opened to spray oil; after the coil is powered off, the balance valve rod moves downwards under the action of the electromagnetic valve reset spring and is pressed on the upper end face of the middle block, the upper cavity of the balance valve rod is communicated with the oil cavity, the oil return hole is disconnected with the oil tank, and meanwhile, fuel in the downlink high-pressure oil way enters the control cavity through the oil inlet throttle hole, the upper cavity of the balance valve rod, the oil cavity and the middle oil duct on the one hand and enters the control cavity through the hydraulic feedback oil duct, the oil cavity and the middle oil duct on the other hand.
3. The diameter of the middle part of the resonance throttling hole is smaller than the diameters of the two ends of the resonance throttling hole and smaller than the diameter of the resonance through hole, and the total axial length of the resonance throttling hole and the resonance through hole is consistent.
The invention has the advantages that: the invention adopts the pressure accumulation cavity structure, and ensures that the continuous oil injection process of the oil injector can not cause great fluctuation to the common rail fuel pressure to influence the oil injection processes of other oil injectors under the condition of large oil injection quantity. The invention adopts the flow-limiting valve component processed with the resonance structure, effectively reduces the occurrence of abnormal oil injection conditions, reduces fuel pressure waves generated by water hammer effect in the oil injector in the oil injection process, and ensures the normal and stable oil injection process. The oil injector adopts the electromagnetic valve to control the balance valve rod to adjust the switch of the oil return way, thereby improving the control precision and the flexibility, effectively improving the discharge of the whole diesel engine and improving the fuel economy. The balance valve rod of the oil sprayer adopts a two-position three-way form, two-way sealing of a conical surface and a plane can be realized, and dynamic oil return amount is reduced. The annular throttle belt and the oil inlet throttle hole at the conical surface of the balance valve rod are matched with the hydraulic feedback oil channel to realize a variable oil injection rule, and the seating response of the needle valve is accelerated. And the static pressure difference does not exist in the oil sprayer, so that the oil sprayer can realize the function of static leakage-free.
Drawings
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a schematic view of a flow restriction valve;
FIG. 3 is a schematic view of a solenoid valve;
FIG. 4 isbase:Sub>A schematic view A-A.
Detailed Description
The invention will now be described in more detail by way of example with reference to the accompanying drawings in which:
referring to fig. 1-4, the main structure of the micro-dynamic oil return resonant electronic control oil injector with hydraulic feedback comprises an oil injector head 1, an oil injector body 14, a flow limiting valve assembly 3, an electromagnetic valve assembly 13, a tightening cap 5, a needle valve limiting sleeve 11, a nozzle 7 and a needle valve body 8. The injector head 1 is screwed to the injector body 14 and is sealed by a sealing ring 15 placed on the injector body 14. The main inlet opening 16 of the injector head 1 communicates with the pressure accumulation chamber 2 in the injector body 14. An electromagnetic valve component 13, a nozzle 7 and a needle valve body 8 are arranged below the oil injector body 14 and are assembled and connected through a fastening cap 5. The flow limiting valve assembly 3 is placed in the oil injector body 14, and mainly comprises a retainer ring 17, a limiting spring seat 30, a damping spring 18, a limiting piston 19, a ball valve 28, a supporting slide block 21, a ball valve return spring 22 and a ball valve return spring seat 26. The flow-limiting piston 19 is provided with a flow-limiting hole 20 and a piston blind hole 29, and the supporting slide block 21 is provided with an axial central through hole 27 to ensure that fuel oil can pass through a lower oil path. Two resonance holes are processed at the bottom of the ball valve reset spring seat 22, namely a resonance throttling hole 25 and a resonance through hole 23. An electromagnetic valve assembly 13 is arranged between the bottom of the oil injector body 14 and the upper part of the nozzle 7, and mainly structurally comprises an electromagnetic valve return spring 31, an electromagnetic valve return spring seat 44, a coil 32, an electromagnet 43, an armature 42, a valve seat 33, an intermediate block 39 and a balance valve rod 41. The armature 42 and the balance valve stem 41 are placed in combination in the valve seat 33, and the oil intake orifice 34 is machined in the valve seat 33. The middle block 39 is internally provided with a hydraulic feedback oil path 33, an oil return hole 37, a middle oil path 38 and the like, and forms a control cavity 6 together with the needle valve limiting sleeve 11 and the needle valve body 8.
Fig. 1 is a schematic view of the overall structure of a fuel injector according to the present invention. A main oil inlet hole 16 is processed on the injector head 1, and high-pressure fuel oil conveyed by a high-pressure oil pipe enters the inside of the injector through the main oil inlet hole 16. The injector head 1 and the injector body 14 are assembled by a thread line, and a sealing ring 15 is arranged between the injector head and the injector body for sealing. The main oil inlet hole 16 communicates with the pressure accumulation chamber 2. The fuel in the accumulator chamber 2 will pass down through the constrictor valve assembly 3. After flowing out from the flow-limiting valve assembly 3, the fuel enters the control cavity 6 and the oil containing groove 10 through the descending high-pressure oil way 4. An electromagnetic valve assembly 13 is arranged between the lower part of the oil sprayer body 14 and the nozzle 7. The lifting and seating of the armature 42 and the balance valve stem 41 are controlled by electromagnetic force within the solenoid valve assembly 13. When the balance valve rod 41 is lifted upwards, the oil return hole 37 is opened, and the fuel in the control chamber 6 flows through the intermediate oil passage 38 into the oil chamber 35 and is discharged through the oil return hole 37. During the raising of the balancing valve stem 41, a small portion of the fuel enters the oil chamber 35 through the fuel inlet orifice 34 and drains to the low pressure tank. This dynamic return is low compared to the dynamic return of a two-position two-way valve. Along with the reduction of the fuel pressure of the control cavity 6, a fuel pressure difference is formed between the control cavity and the oil containing groove 10, so that the needle valve body 8 overcomes the spring pretightening force of the needle valve return spring 12 to lift, and oil injection starts. Wherein the displacement of the needle valve body 8 is limited by the needle valve stop collar 11. When the balance valve rod 41 is seated downwards, the oil return hole 37 is closed, fuel oil flows through the oil inlet throttle hole 34 and the hydraulic feedback oil channel 36, flows through the balance valve rod 41, the oil cavity 35 and the intermediate oil channel 38 and enters the control cavity 6, so that the control cavity 6 is pressurized, the needle valve body 8 is seated under the spring pre-tightening force of the needle valve return spring 12, and the oil injection process is finished. In the nozzle 7,base:Sub>A needle valve body 8 is placed which is pressed bybase:Sub>A needle valve return spring 12, and as shown in fig. 4, an enlarged view ofbase:Sub>A sectionbase:Sub>A-base:Sub>A of the needle valve body 8. The arc-shaped surface of the needle valve body 8 can play a good role in guiding. And no static pressure difference exists in the nozzle 7, so that the characteristic of no static leakage of the oil injector is ensured. The nozzle 7 and the solenoid valve assembly 13 are placed in the tightening cap 5 and are fastened to the injector body 14 by means of a thread.
Fig. 2 is a schematic view of a portion of a constrictor valve assembly of the present invention. The flow-limiting valve assembly 3 mainly comprises a check ring 17, a limiting spring seat 30, a damping spring 18, a flow-limiting piston 19, a ball valve 28, a supporting slide block 21, a ball valve return spring 22, a ball valve return spring seat 26 and the like. The entire restrictor valve assembly 3 is arranged inside the injector body 14 via the pressure accumulation chamber 2 and is restricted by the stop ring 17. The limit spring seat 30 cooperates with the retainer ring 17 to act as a spring seat for the damping spring 18 on the one hand and to limit the maximum displacement of the limiting piston 19 on the other hand. By the spring preload of the damping spring 18 and the ball valve return spring 22, the ball valve 28 cooperates with the lower end face of the flow-limiting piston 19 and the upper end face of the support slider 21. Ball return spring seat 26 is biased by the force of ball return spring 22 to a bottom position, the upper variable cross-section of which is the seating surface of ball 28. From the pressure accumulation chamber 2, the fuel enters a blind piston bore 29 in the metering piston 19 and then, via the metering orifice 20, enters the axially central through-bore 27 of the support slide 21. The fuel flowing out of the axial central through hole 27 passes through the resonance through hole 23 and the resonance orifice 25 into the transition oil chamber 24. The provision of the machined resonant through-holes 23 and the resonant orifice 25 allows the amplitude of the fuel pressure wave passing through the two holes to be reduced. Because there is one section aperture in resonance orifice 25 to be littleer than resonance through-hole 23, its throttle effect is stronger, causes the fuel velocity of flow that flows through from two holes to be different for the fuel pressure wave of original looks produces the phase difference, and two strands of fuel pressure waves offset each other after the stack, and the pressure fluctuation further reduces, and two holes are the same in axial total length. The descending high-pressure oil path 4 is communicated with the transition oil chamber 24 and communicated with the lower oil path. When the oil injector injects oil normally, the fuel is sprayed out of the spray hole 9, and the pressure of the fuel in the transition oil cavity 24 is reduced. Due to the throttling effect of the throttling hole 20 on the fuel, the pressure of the fuel in the piston blind hole 29 in the throttling piston 19 and the pressure accumulation cavity 2 is high, and a pressure difference is formed between the pressure accumulation cavity and the transition oil cavity 24, so that the throttling piston 19, the ball valve 28 and the supporting slide block 21 are displaced downwards, the fuel sprayed by the fuel injector is compensated, and the ball valve 28 is not seated on the ball valve reset spring seat 26. When the oil injection is finished, the pressure difference between the upper part and the lower part of the flow-limiting piston 19 is gradually reduced along with the flowing of the fuel through the flow-limiting hole 20, and the flow-limiting piston 19, the ball valve 28 and the supporting slide block 21 are restored to the original positions under the action of the return spring force of the ball valve. When the spray holes 9 continuously spray fuel, the mass of the discharged fuel exceeds a threshold value, and the fuel injector is in an abnormal working state, the oil pressure of the transition oil cavity 24 below the flow-limiting piston 19 is rapidly reduced due to the large flow and the high flow speed of the fuel sprayed by the spray holes 9, so that an up-down pressure difference is formed, the flow-limiting piston 19 compresses the ball valve 28 to be seated on the ball valve reset spring seat 26, and the fuel is prevented from flowing. Due to the lack of fuel supply, the injector stops operating, preventing continuation of abnormal fuel injection.
Fig. 3 is a schematic view of a part of the structure of the solenoid valve assembly of the present invention. The solenoid valve assembly 13 mainly includes a solenoid valve return spring seat 44, a solenoid valve return spring 31, a coil 32, an electromagnet 43, an armature 42, a balance valve rod 41, a valve seat 33, and an intermediate block 39. The solenoid valve return spring seat 44, the solenoid valve return spring 31, the coil 32 and the electromagnet 43 are built inside the injector body 14, wherein the solenoid valve return spring seat 44 is fastened to the topmost end of the solenoid valve by threads. Between the solenoid valve return spring seat 44 and the armature 42 is the solenoid valve return spring 31. The armature 42 and the balancing stem 41 are placed inside the valve seat 33 below the injector body 14. The part that joins the valve seat 33 at the bottom is an intermediate block 39. The whole electromagnetic valve is in the form of a two-position three-way valve. When the injector is not in operation, an annular throttle band 40 is present between the conical surface of the balancing stem 41 and the conical junction surface of the valve seat 33. When the injector starts to inject oil, the coil 32 of the electromagnetic valve is electrified to form a magnetic loop with the electromagnet 43 and the armature 42, so that electromagnetic force is generated, and the balance valve rod 41 is attracted to move upwards. The equivalent flow area of the annular throttle band 40 is denoted as A1, the effective flow area of the oil inlet orifice 34 is denoted as A2, and A1 is larger than A2 when the injector is not operating. During the upward movement of the balance valve rod 41, the throttle area A1 of the annular throttle belt 40 is continuously reduced to 0. When A1 is larger than A2, the throttling effect is mainly realized by the oil inlet throttling hole 34, and the speed of the control cavity 6 for releasing pressure to the oil return hole 37 through the intermediate oil passage 38 is fixed; when A1 is smaller than A2, the throttling effect is mainly realized by the annular throttling belt 40, the throttling effect is more and more obvious as the throttling area A1 of the annular throttling belt 40 is continuously reduced, the pressure relief speed of the control cavity 6 through the middle oil duct 38 is faster and faster, and the oil injection speed is gradually increased; when the balance valve rod 41 moves to be completely matched with the conical surface of the valve seat 33, the oil is not fed into the oil feeding throttling hole 34, the oil drainage speed of the control cavity 6 reaches the maximum, and the oil injection speed reaches the maximum. In the whole oil injection process, high-pressure fuel oil always enters the oil cavity 35 formed by the valve seat 33 and the balance valve rod 41 through the hydraulic feedback oil channel 36, the oil drainage rate of the oil cavity 35 and the control cavity 6 is slowed down, the pressure drop of the control cavity 6 at the initial oil injection stage is reduced and slowed down, and the generation of nitrogen oxides is reduced. At the end of oil injection, the hydraulic feedback oil passage 36 accelerates the pressure building speed of the control cavity 6, and improves the seating response of the needle valve body 8.
According to the working process, in the oil injection process of the micro-dynamic oil return resonant type electric control oil injector with hydraulic feedback, a form of a two-position three-way valve is adopted, and the dynamic oil return amount of fuel oil in the oil injection process is reduced by balancing the oil inlet at the valve rod 41 and the oil inlet inside the middle block 39 through the electromagnetic valve. The whole oil injection process is controlled by an electromagnetic valve, and the balance valve rod 41 is driven to move by electromagnetic force, so that the requirements of high response speed, high control precision and variable oil injection rule in the oil injection process are met. The annular throttle band 40 and the oil inlet orifice 34 at the conical surface of the balance valve stem cooperate with the hydraulic feedback oil passage 36 to achieve a slow-to-fast variable oil injection law at the start of oil injection and to accelerate the seating response of the needle valve. The fuel injector body 14 is internally provided with the flow limiting valve assembly 3 with a resonance structure, so that the continuous operation of an abnormal fuel injection state is prevented, the fuel pressure fluctuation is reduced, and the stability of the working process is ensured. When the common rail pressure storage cavity is applied to a common rail system, the pressure storage cavity 2 can effectively reduce the pressure fluctuation of the common rail under the large-oil-volume injection state, so that the phenomenon of reduction of uniformity and consistency in the oil injection process of each cylinder is reduced.
Claims (3)
1. A micro-dynamic oil return resonant type electric control oil injector with hydraulic feedback is characterized in that: the oil sprayer comprises an oil sprayer head, an oil sprayer body, a flow limiting valve assembly, a solenoid valve assembly, a needle valve assembly and a downlink high-pressure oil way, wherein the oil sprayer head is arranged above the oil sprayer body, a main oil inlet hole is formed in the oil sprayer head, a pressure storage cavity is formed in the oil sprayer body, the main oil inlet hole is communicated with the pressure storage cavity, the flow limiting valve assembly is arranged in the pressure storage cavity, the solenoid valve assembly and the needle valve assembly are sequentially arranged at the lower end of the oil sprayer body, a tightening cap is positioned outside the solenoid valve assembly and the needle valve assembly, and the upper end of the tightening cap is connected with the lower end of the oil sprayer body in a threaded connection mode;
the flow limiting valve assembly comprises a limiting spring seat, a flow limiting piston, a ball valve reset spring seat and a supporting slide block, wherein the limiting spring seat, the flow limiting piston and the ball valve reset spring seat are arranged from top to bottom;
the electromagnetic valve assembly comprises an electromagnet, a coil, an armature, a balance valve rod, a valve seat and an intermediate block, wherein the coil is wound on the electromagnet, an electromagnetic valve reset spring seat is arranged above the electromagnet, the armature is arranged below the electromagnet, an electromagnetic valve reset spring is arranged between the armature and the electromagnetic valve reset spring seat, the balance valve rod is positioned in the valve seat, the upper end part of the balance valve rod is fixedly connected with the armature, the intermediate block is arranged below the valve seat, a balance valve rod upper cavity is formed between the middle part of the balance valve rod and the valve seat, an oil cavity is formed between the lower end part of the balance valve rod, the valve seat and the intermediate block, an oil inlet orifice is arranged in the valve seat, an oil return hole, an intermediate oil passage and a hydraulic feedback oil passage are arranged in the intermediate block, the oil inlet orifice is communicated with the balance valve rod upper cavity, the intermediate oil passage and the hydraulic feedback oil passage are respectively and directly communicated with or disconnected with the oil tank under the control of the balance valve rod; an annular throttle belt is arranged between the conical surface of the balance valve rod and the conical joint surface of the valve seat, the equivalent flow area of the annular throttle belt is A1, the effective flow area of the oil inlet throttle hole is A2, A1 is larger than A2 when the oil sprayer does not work, and A1 is continuously reduced until the equivalent flow area is 0 in the upward movement process of the balance valve rod; the needle valve assembly comprises a needle valve limiting sleeve, a nozzle and a needle valve body, the needle valve limiting sleeve is positioned in the nozzle, the upper part of the needle valve body is positioned in the needle valve limiting sleeve, the lower part of the needle valve body is positioned in the nozzle, a control cavity is formed between the upper part of the needle valve body and the needle valve limiting sleeve, a bulge is arranged on the needle valve limiting sleeve and positioned at the control cavity, a needle valve reset spring is arranged between the needle valve body and the bulge, the control cavity is communicated with a middle oil duct, an oil containing groove is formed between the needle valve body and the nozzle, and the end part of the nozzle is provided with a spray hole;
the upper end of the downlink high-pressure oil way is communicated with a transition oil cavity and is communicated with an oil containing groove through an oil sprayer body, a valve seat, a middle block and a nozzle, and an oil inlet throttling hole and a hydraulic feedback oil way are respectively communicated with the downlink high-pressure oil way;
when the spray hole sprays oil, the fuel pressure of the transition oil cavity is reduced, the flow-limiting piston, the ball valve and the supporting slide block integrally move downwards, the ball valve is not seated on the ball valve reset spring seat, and the flow-limiting hole is communicated with the axial central through hole; when the mass of the fuel flowing out of the spray hole exceeds a threshold value, the flow limiting piston compresses the ball valve and enables the ball valve to be seated on a ball valve reset spring seat, and the flow limiting hole is disconnected with the axial central through hole; when the spray hole stops spraying oil, the flow-limiting piston, the ball valve and the supporting slide block are integrally restored to the initial positions under the action of the ball valve return spring.
2. The micro-dynamic oil return resonant electronic control oil injector with hydraulic feedback as claimed in claim 1, characterized in that: when the coil is electrified, the balance valve rod moves upwards, the upper cavity of the balance valve rod is in a disconnected state with the oil cavity, the oil return hole is in a communicated state with the oil tank, fuel oil in the control cavity returns to the oil tank through the middle oil duct and the oil return hole, the needle valve body is lifted upwards, and the spray hole is opened to spray oil; after the coil is powered off, the balance valve rod moves downwards under the action of the electromagnetic valve reset spring and is pressed on the upper end surface of the middle block, the upper cavity of the balance valve rod is communicated with the oil cavity, the oil return hole is disconnected with the oil tank, and meanwhile, fuel in the downlink high-pressure oil way enters the control cavity through the oil inlet throttling hole, the upper cavity of the balance valve rod, the oil cavity and the middle oil duct on the one hand and enters the control cavity through the hydraulic feedback oil duct, the oil cavity and the middle oil duct on the other hand.
3. The micro-dynamic oil return resonant type electric control oil injector with hydraulic feedback as claimed in claim 1 or 2, is characterized in that: the diameter of the middle part of the resonance throttling hole is smaller than the diameters of the two ends of the resonance throttling hole and smaller than the diameter of the resonance through hole, and the total axial length of the resonance throttling hole and the resonance through hole is consistent.
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| CN109099192A (en) * | 2018-09-21 | 2018-12-28 | 英嘉动力科技无锡有限公司 | A kind of novel two-position three-way valve |
| CN114151252B (en) * | 2021-11-19 | 2023-07-21 | 哈尔滨工程大学 | Liquid ammonia phase change cooling type hybrid power thermal management system |
| CN114458498B (en) * | 2022-02-24 | 2022-10-28 | 哈尔滨工程大学 | High-pressure common rail oil injector for realizing high-stability injection based on throttling resistance-capacitance effect |
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